US4231548A - Balance valve disc and seat structure - Google Patents

Balance valve disc and seat structure Download PDF

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Publication number
US4231548A
US4231548A US05/930,223 US93022378A US4231548A US 4231548 A US4231548 A US 4231548A US 93022378 A US93022378 A US 93022378A US 4231548 A US4231548 A US 4231548A
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US
United States
Prior art keywords
disc
chamber
valve disc
responsive means
pressure responsive
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Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
US05/930,223
Inventor
Heinz W. Braukmann
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Braukmann Armaturen AG
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Braukmann Armaturen AG
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Filing date
Publication date
Application filed by Braukmann Armaturen AG filed Critical Braukmann Armaturen AG
Priority to US05/930,223 priority Critical patent/US4231548A/en
Application granted granted Critical
Publication of US4231548A publication Critical patent/US4231548A/en
Assigned to HONEYWELL INC., A CORP. OF DE reassignment HONEYWELL INC., A CORP. OF DE EFFECTIVE DATE 4-1-80 Assignors: BRAUKMANN ARMATUREN AG
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K39/00—Devices for relieving the pressure on the sealing faces
    • F16K39/02—Devices for relieving the pressure on the sealing faces for lift valves
    • G—PHYSICS
    • G05—CONTROLLING; REGULATING
    • G05D—SYSTEMS FOR CONTROLLING OR REGULATING NON-ELECTRIC VARIABLES
    • G05D16/00—Control of fluid pressure
    • G05D16/04—Control of fluid pressure without auxiliary power
    • G05D16/06—Control of fluid pressure without auxiliary power the sensing element being a flexible membrane, yielding to pressure, e.g. diaphragm, bellows, capsule
    • G05D16/063—Control of fluid pressure without auxiliary power the sensing element being a flexible membrane, yielding to pressure, e.g. diaphragm, bellows, capsule the sensing element being a membrane
    • G05D16/0644—Control of fluid pressure without auxiliary power the sensing element being a flexible membrane, yielding to pressure, e.g. diaphragm, bellows, capsule the sensing element being a membrane the membrane acting directly on the obturator
    • G05D16/0655—Control of fluid pressure without auxiliary power the sensing element being a flexible membrane, yielding to pressure, e.g. diaphragm, bellows, capsule the sensing element being a membrane the membrane acting directly on the obturator using one spring-loaded membrane
    • G05D16/0658—Control of fluid pressure without auxiliary power the sensing element being a flexible membrane, yielding to pressure, e.g. diaphragm, bellows, capsule the sensing element being a membrane the membrane acting directly on the obturator using one spring-loaded membrane characterised by the form of the obturator
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/7722—Line condition change responsive valves
    • Y10T137/7781—With separate connected fluid reactor surface
    • Y10T137/7793—With opening bias [e.g., pressure regulator]
    • Y10T137/7801—Balanced valve

Definitions

  • This invention relates to valve structures wherein a valve disc, co-operating with a valve seat is balanced in order to eliminate the effect of varying pressure in the valve during operation of the valve disc in order that fluid can be withdrawn at a constant predetermined pressure.
  • Balanced valves of this type are used particularly in pressure reducers.
  • Balanced valve structures have been developed because apart from inability to provide a consistent reduced pressure a non-balanced single seat valve has a reduced ability to perform as required when there are small pressure differences between initial and reduced pressures. Furthermore, a smaller valve seat, normally found on non-balanced single seat valves, is necessary to reduce the tendency to audible operation which is particularly objectionable in residential installations.
  • the balanced single valve of the invention has a hollow disc co-operating with a valve seat, with the interior of the disc supporting movable pressure responsive means such as a flexible diaphragm or a piston with a seal.
  • the pressure responsive means divides the disc into a first and second chamber, each having apertures whereby the first chamber communicates with the inlet side of the valve and the second chamber communicates with the outlet side of the valve.
  • the pressure responsive means is secured to one end of a plunger which extends through the second chamber and then through the valve seat, with means, such as a valve body, engaging the other end of the plunger when the first chamber has a higher pressure than the second chamber.
  • FIG. 1 is a cross section of one embodiment of a valve structure of the invention wherein the pressure responsive means in a single valve disc is a diaphragm;
  • FIG. 2 is a cross section of another embodiment of a valve structure of the invention wherein the pressure responsive means in the single valve disc is a piston with a seal;
  • FIG. 3 is a cross section of a pressure reducing valve incorporating the valve structure shown in FIG. 1.
  • valve structure of the invention shown therein has a hollow valve disc, generally denoted by the numeral 10, constructed of an inverted cup shaped member 12, having a side wall 14, which is internally threaded as shown.
  • the base of the inverted cup shaped member 12 has a centrally disposed integral valve stem 16 extending upwards therefrom.
  • the valve disc stem also has a U shaped member 17 with an externally threaded side wall 18 which is in engagement with the threads of the side wall 14 of the cup shaped member 12.
  • the base of the U shaped member 17 has an integral downwardly extending centrally disposed hollow boss 19 which has a stepped externally threaded portion 20.
  • An internally threaded collar 22 is engageable on the stepped portion 20 of the boss 19.
  • the collar 22 and the boss 19 support a resilient disc 24 which bears against the base of the U shaped member 17.
  • the resilient disc 24 engages a valve seat 26 when the valve structure is in the closed position illustrated in FIG. 1.
  • a flexible diaphragm 28 is horizontally positioned in the hollow disc 10 and is held in place, as shown in FIG. 1, by peripheral engagement between the inverted cup shaped member 12 and the U shaped member 17 when they are threaded together.
  • the flexible diaphragm 28 divides the hollow disc 10 into a first chamber 30 and a second chamber 32.
  • the inverted cup shaped member 12 has apertures 34 which provide for fluid pressure communication between the first chamber 30 and the upper side of the hollow disc 10, i.e. above the valve seat 26.
  • a plate 36 is secured to the underside of the flexible diaphragm 28 and the upper end of a plunger 38 is secured to the underside of the plate 36.
  • the plunger 38 extends downwards through the second chamber 32 of the hollow disc 10 and then through the hollow boss 19 in spaced relationship therefrom, thereby forming an aperture 40 which provides for fluid pressure communication between the second chamber 32 and the lower side of the hollow disc 10, i.e. below the valve seat 26.
  • the lower end of the plunger 38 is engageable with stop means 42 when the pressure in the first chamber 30 is higher than the pressure in the second chamber 32.
  • the flexible diaphragm 28 is replaced by a piston 44 and seal 46 engageable with the internal side wall 48 of the hollow disc 10. Again when the pressure in the first chamber 30 is higher than the pressure in the second chamber 32, the pressure on the piston 44 is transmitted to the supported plunger 49 and removed from the disc 10.
  • FIG. 3 shows how the valve structure of FIG. 1 may be incorporated into a pressure reducer which has a hollow valve body, generally denoted by the numberal 50, constructed of a lower portion 52 surmounted by a removable cap 54 sealingly secured together through flanges 56 and 58 respectively by cap screws 60.
  • the lower portion 52 of the valve body 50 has an inlet 62 communicating with an outlet 64 when the hollow valve disc 10 is in the open position.
  • the inlet 62 and the outlet 64 are separated by an integral annular inner wall 66 to valve body 10 with the inner wall 66 conveniently forming the valve seat 26.
  • the upper removable cap 54 has a pressure inlet 68 positioned below another annular wall 70 which is traversed by the valve stem 16, the latter terminating in an integral shoulder 72.
  • One end of a helical spring 74 bears against the underside of the shoulder 72 and the other end of the spring 74 bears against the upper side of the annular wall 70.
  • An annular diaphragm 76 is secured at its periphery by the flanges 56 and 58; the diaphragm 76 is secured to valve stem 16 by opposed plates 78 and 80.
  • the lower wall 82 of the valve body 50 is preferably grooved as at 84 to provide for location of the lower end of the plunger 28.
  • the lower wall 82 acts as a stop means for the plunger 28 when the pressure in the first chamber 30 is higher than the pressure in the second chamber 32 of the valve disc 10. As a result the pressure necessary to lift the hollow valve disc 10 is minimally the same despite variations in the inlet pressure.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Fluid Mechanics (AREA)
  • General Physics & Mathematics (AREA)
  • Automation & Control Theory (AREA)
  • Control Of Fluid Pressure (AREA)

Abstract

A balanced valve disc and seat structure has a hollow valve disc engageable with the seat and pressure responsive means supported in the disc; the pressure responsive means divides the hollow valve disc into separate first and second chambers with a first aperture in the disc communicating with the first chamber and a second aperture in the disc communicating with the second chamber. A plunger has one end secured to the pressure responsive means with the other end of the plunger extending through the second chamber and the valve seat with means engaging the other end of the plunger when the first chamber has a higher pressure than the second chamber.

Description

FIELD OF INVENTION
This invention relates to valve structures wherein a valve disc, co-operating with a valve seat is balanced in order to eliminate the effect of varying pressure in the valve during operation of the valve disc in order that fluid can be withdrawn at a constant predetermined pressure. Balanced valves of this type are used particularly in pressure reducers.
PRIOR ART
Balanced valve structures have been developed because apart from inability to provide a consistent reduced pressure a non-balanced single seat valve has a reduced ability to perform as required when there are small pressure differences between initial and reduced pressures. Furthermore, a smaller valve seat, normally found on non-balanced single seat valves, is necessary to reduce the tendency to audible operation which is particularly objectionable in residential installations.
SUMMARY OF THE INVENTION
The balanced single valve of the invention has a hollow disc co-operating with a valve seat, with the interior of the disc supporting movable pressure responsive means such as a flexible diaphragm or a piston with a seal. The pressure responsive means divides the disc into a first and second chamber, each having apertures whereby the first chamber communicates with the inlet side of the valve and the second chamber communicates with the outlet side of the valve. The pressure responsive means is secured to one end of a plunger which extends through the second chamber and then through the valve seat, with means, such as a valve body, engaging the other end of the plunger when the first chamber has a higher pressure than the second chamber.
As a result of this arrangement, the pressure in the first chamber of the disc affects the pressure responsive means and not the disc; thus variations of pressure in the valve body have no effect on the disc and it takes the same minimum force to lift the valve disc from the seat in all circumstances.
BRIEF DESCRIPTION OF THE DRAWINGS
FIG. 1 is a cross section of one embodiment of a valve structure of the invention wherein the pressure responsive means in a single valve disc is a diaphragm;
FIG. 2 is a cross section of another embodiment of a valve structure of the invention wherein the pressure responsive means in the single valve disc is a piston with a seal;
FIG. 3 is a cross section of a pressure reducing valve incorporating the valve structure shown in FIG. 1.
DESCRIPTION OF THE PREFERRED EMBODIMENTS OF THE INVENTION
With reference to FIG. 1, the embodiment of the valve structure of the invention shown therein has a hollow valve disc, generally denoted by the numeral 10, constructed of an inverted cup shaped member 12, having a side wall 14, which is internally threaded as shown. The base of the inverted cup shaped member 12 has a centrally disposed integral valve stem 16 extending upwards therefrom.
The valve disc stem also has a U shaped member 17 with an externally threaded side wall 18 which is in engagement with the threads of the side wall 14 of the cup shaped member 12. The base of the U shaped member 17 has an integral downwardly extending centrally disposed hollow boss 19 which has a stepped externally threaded portion 20. An internally threaded collar 22 is engageable on the stepped portion 20 of the boss 19. The collar 22 and the boss 19 support a resilient disc 24 which bears against the base of the U shaped member 17. The resilient disc 24 engages a valve seat 26 when the valve structure is in the closed position illustrated in FIG. 1.
A flexible diaphragm 28 is horizontally positioned in the hollow disc 10 and is held in place, as shown in FIG. 1, by peripheral engagement between the inverted cup shaped member 12 and the U shaped member 17 when they are threaded together. The flexible diaphragm 28 divides the hollow disc 10 into a first chamber 30 and a second chamber 32.
The inverted cup shaped member 12 has apertures 34 which provide for fluid pressure communication between the first chamber 30 and the upper side of the hollow disc 10, i.e. above the valve seat 26.
A plate 36 is secured to the underside of the flexible diaphragm 28 and the upper end of a plunger 38 is secured to the underside of the plate 36. The plunger 38 extends downwards through the second chamber 32 of the hollow disc 10 and then through the hollow boss 19 in spaced relationship therefrom, thereby forming an aperture 40 which provides for fluid pressure communication between the second chamber 32 and the lower side of the hollow disc 10, i.e. below the valve seat 26.
The lower end of the plunger 38 is engageable with stop means 42 when the pressure in the first chamber 30 is higher than the pressure in the second chamber 32.
With reference to FIG. 2 the flexible diaphragm 28 is replaced by a piston 44 and seal 46 engageable with the internal side wall 48 of the hollow disc 10. Again when the pressure in the first chamber 30 is higher than the pressure in the second chamber 32, the pressure on the piston 44 is transmitted to the supported plunger 49 and removed from the disc 10.
FIG. 3 shows how the valve structure of FIG. 1 may be incorporated into a pressure reducer which has a hollow valve body, generally denoted by the numberal 50, constructed of a lower portion 52 surmounted by a removable cap 54 sealingly secured together through flanges 56 and 58 respectively by cap screws 60. The lower portion 52 of the valve body 50 has an inlet 62 communicating with an outlet 64 when the hollow valve disc 10 is in the open position. The inlet 62 and the outlet 64 are separated by an integral annular inner wall 66 to valve body 10 with the inner wall 66 conveniently forming the valve seat 26.
The upper removable cap 54 has a pressure inlet 68 positioned below another annular wall 70 which is traversed by the valve stem 16, the latter terminating in an integral shoulder 72. One end of a helical spring 74 bears against the underside of the shoulder 72 and the other end of the spring 74 bears against the upper side of the annular wall 70. An annular diaphragm 76 is secured at its periphery by the flanges 56 and 58; the diaphragm 76 is secured to valve stem 16 by opposed plates 78 and 80.
The lower wall 82 of the valve body 50 is preferably grooved as at 84 to provide for location of the lower end of the plunger 28. The lower wall 82 acts as a stop means for the plunger 28 when the pressure in the first chamber 30 is higher than the pressure in the second chamber 32 of the valve disc 10. As a result the pressure necessary to lift the hollow valve disc 10 is minimally the same despite variations in the inlet pressure.

Claims (6)

I claim:
1. A balanced valve disc and seat structure having a hollow valve disc engageable with said seat, pressure responsive means supported in said disc, said pressure responsive means dividing said hollow valve disc into separate first and second chambers, a first aperture in said disc communicating with said first chamber, a second aperture in said disc communicating with said second chamber, a plunger having one end secured to said pressure responsive means, the other end of said plunger extending through said second chamber and said valve seat and means engaging said other end of said plunger when said first chamber has a higher pressure than said second chamber.
2. A balanced valve disc and seat structure according to claim 1 wherein said pressure responsive means is a diaphragm.
3. A balanced valve disc and seat structure according to claim 1 wherein said pressure responsive means is a piston with a seal engageable with the interior wall of said hollow valve disc.
4. A balanced valve disc and seat structure according to claim 1 wherein said hollow valve disc is constructed of a pair of cup shaped members with one threaded into the other.
5. A balanced valve disc and seat structure according to claim 4 wherein said pressure responsive means is a diaphragm held between said pair of cup shaped members.
6. A balanced valve disc and seat structure according to claim 4 wherein said pressure responsive means is a piston with a seal engageable with the inner wall formed by said pair of cup shaped members in threaded engagement.
US05/930,223 1978-08-02 1978-08-02 Balance valve disc and seat structure Expired - Lifetime US4231548A (en)

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8820703B2 (en) * 2007-09-13 2014-09-02 John Leslie Johnson Double action directional fluid flow valve
US10865907B2 (en) 2018-03-08 2020-12-15 Buerkert Werke Gmbh & Co. Kg Solenoid valve

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB244923A (en) * 1925-01-06 1925-12-31 James Keith & Blackman Company Non-return gas supply valve
US2087037A (en) * 1935-02-21 1937-07-13 Klipfel Mfg Company Valve
US2622613A (en) * 1947-06-02 1952-12-23 Andale Co Pressure control valve
US3011521A (en) * 1960-02-04 1961-12-05 Buford R Smith Valve
US3554611A (en) * 1968-04-06 1971-01-12 Aisin Seiki Hydraulic brake pressure control assembly
US3873063A (en) * 1973-11-01 1975-03-25 Kieley & Mueller Aspirated balance piston

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB244923A (en) * 1925-01-06 1925-12-31 James Keith & Blackman Company Non-return gas supply valve
US2087037A (en) * 1935-02-21 1937-07-13 Klipfel Mfg Company Valve
US2622613A (en) * 1947-06-02 1952-12-23 Andale Co Pressure control valve
US3011521A (en) * 1960-02-04 1961-12-05 Buford R Smith Valve
US3554611A (en) * 1968-04-06 1971-01-12 Aisin Seiki Hydraulic brake pressure control assembly
US3873063A (en) * 1973-11-01 1975-03-25 Kieley & Mueller Aspirated balance piston

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8820703B2 (en) * 2007-09-13 2014-09-02 John Leslie Johnson Double action directional fluid flow valve
US9395016B2 (en) 2007-09-13 2016-07-19 John Leslie Johnson Double action direction fluid flow valve
US9587757B2 (en) 2007-09-13 2017-03-07 John Leslie Johnson Double action direction fluid flow valve
US9841116B2 (en) 2007-09-13 2017-12-12 John Leslie Johnson Double action direction fluid flow valve
US11079036B2 (en) 2007-09-13 2021-08-03 John Leslie Johnson Double action direction fluid flow valve
US10865907B2 (en) 2018-03-08 2020-12-15 Buerkert Werke Gmbh & Co. Kg Solenoid valve

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